Compliant bearing

ABSTRACT

A first embodiment of a compliant bearing includes a main body and a bearing surface. The main body and the bearing surface may be engaged with one another via one or more bearing surface springs configured such that the bearing surface is compliant with respect to the main body. A second embodiment of a compliant bearing includes a main body and at least one bearing pad. The main body and the bearing pad may be engaged with one another via one or more pad radial and/or pad axial springs configured such that the bearing pad is compliant with respect to the main body. A sensor web may be integrated into the compliant bearing. In one embodiment the sensor web comprises at least one sensor configured as a strain gauge and affixed to a bearing surface spring.

CROSS REFERENCE TO RELATED APPLICATION

This patent application claims priority from and is a continuation-in-part of U.S. patent application Ser. No. 12/962,430 filed on Dec. 7, 2010 now abandoned, which claimed priority from and was a continuation of U.S. patent application Ser. No. 11/787,146, filed on Apr. 13, 2007, now U.S. Pat. No. 7,845,855; this patent application also claims priority from and is a continuation-in-part of U.S. patent application Ser. No. 11/998,279 filed on Nov. 29, 2007 now abandoned; this patent application also claims priority from and is a continuation-in-part of U.S. patent application Ser. No. 12/793,983 filed on Jun. 4, 2010 now U.S. Pat. No. 8,408,802, which claimed priority from provisional U.S. Pat. App. No. 61/217,989 filed on Jun. 8, 2009; this patent application also claims priority from and is a continuation-in-part of U.S. patent application Ser. No. 13/005,997 filed on Jan. 13, 2011, all of which are incorporated by reference herein in their entireties. Applicant also claims priority from provisional U.S. Pat. App. No. 61/387,274 filed on Sep. 28, 2010 which is incorporated by reference herein in its entirety.

FIELD OF INVENTION

The present invention relates to bearings, and more specifically, compliant bearings and sensor webs for use therewith.

STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH OR DEVELOPMENT

No federal funds were used to develop or create the invention disclosed and described in the patent application.

REFERENCE TO SEQUENCE LISTING, A TABLE, OR A COMPUTER PROGRAM LISTING COMPACT DISK APPENDIX

Not Applicable

BACKGROUND OF THE INVENTION

Rotational bearings are very well known in the art to provide an interface between a rotating structure and a contact surface. It is common to employ some type of pad or pads at the interface to optimize the interconnection between the bearing and the rotating structure and to transmit axial and/or radial forces, which may be accomplished through providing compliance within the bearing in those respective directions.

Load capacity is highly dependent on the pad interface in a bearing. It has been found that the interface may be optimized for better transmission of axial thrust forces by tilting the pads of a bearing or otherwise providing a compliant contact to reduce the amount of friction. Such increasing load capacity by reduced friction may be achieved by controlled hydroplaning Typically, compliant arrangements include an array of fixed pads that are all tilted in a given rotational direction, such as a forward rotational direction. This is advantageous in that hydroplaning may be achieved.

In the prior art, it is well know that the very low viscosity of gas lubricant causes a gas thrust bearing to run at very thin film thickness to support thrust load generated in the rotating machines. However, a known drawback is that any misalignments or geometrical tolerances (such as warping) of rotating shaft collar and/or bearing surface negatively impacts the thrust load capability of the bearing. This runs counter to the continual desire to increase load capacity of the bearing. Further, any thermal distortion or deflection of the shaft collar and/or \bearing surface during operation is another factor that influences the thrust load capability of the bearing.

A spiral grooved thrust bearing typically has the best load capability among all hydrodynamic gas thrust bearings. However, the fact that negative damping may be generated at certain operating conditions (combination of speed and thrust load) is a major drawback of such spiral groove thrust bearings. This behavior of spiral grooved gas thrust bearings is another factor that undesirably limits load capacity of a bearing.

There is a need for a compliant bearing with increased load capacity.

There is a need for a thrust bearing with axial compliance.

There is a need for a compliant bearing with axial damping.

There is a need for a compliant bearing that is more stable than prior art compliant bearings.

There is a need for a thrust bearing with some type of axial compliance to help maintain a proper film thickness by allowing deformation and/or tilt of compliant bearing surface as need of rotating runner surface.

There is a need to provide axial compliance of a thrust bearing to increase the overall load capacity of the bearing.

There is a need to monitor the performance and/or operating conditions on any compliant bearing, radial, axial, or otherwise.

BRIEF DESCRIPTION OF THE DRAWINGS

In order that the advantages of the invention will be readily understood, a more particular description of the invention briefly described above will be rendered by reference to specific preferred embodiments illustrated in the appended drawings. Understanding that these drawings depict only typical embodiments of the invention and are not therefore to be considered limited of its scope, the invention will be described and explained with additional specificity and detail through the use of the accompanying drawings.

FIG. 1 provides an exploded perspective view of a first embodiment of a compliant bearing and a shaft and shaft collar, wherein the compliant bearing is configured as a groove thrust bearing.

FIG. 1A provides a side view of the embodiment of the compliant bearing shown in FIG. 1.

FIG. 1B provides a cross-sectional view of the embodiment of the compliant bearing shown in FIG. 1.

FIG. 1C provides a cross-sectional view of the embodiment of the compliant bearing shown in FIG. 1, wherein damping material has been added to the interstitial areas.

FIG. 2 provides a perspective view of a second embodiment of the compliant bearing, wherein the compliant bearing is configured as a pad thrust bearing.

FIG. 3 provides an axial view of the second embodiment of the compliant bearing.

FIG. 3A provides a side view of the second embodiment of the compliant bearing.

FIG. 3B provides a cross-sectional view of the second embodiment of the compliant bearing.

FIG. 4 provides a graph comparing the increased load capacity of the compliant bearing with that of prior art bearings.

FIG. 5 provides a perspective view of a third embodiment of a compliant bearing with a sensor web configured for use therewith, wherein the compliant bearing is configured as a multi-compliant bearing.

FIG. 5A provides a detailed perspective view of one embodiment of a bearing pad that may be used with the third embodiment of compliant bearing.

FIG. 5B provides a cross-sectional view of one embodiment of a post that may be used with the embodiment of a bearing pad shown in FIG. 5A.

FIG. 6 provides a detailed view of one embodiment of a compliant bearing incorporating one embodiment of a sensor web.

DETAILED DESCRIPTION-LISTING OF ELEMENTS ELEMENT DESCRIPTION ELEMENT # Shaft  4 Shaft collar  6 Groove thrust bearing 10 Pad thrust bearing 12 Main body 14 Multi-compliant bearing 16 Bearing surface 20 Groove pattern 22 First bearing surface spring 24 Second bearing surface spring 26 Interstitial area 28 Damping material 29 Bearing pad 30 Bearing pad interface 32 Pad radial spring 34 Pad axial spring 36 Interstitial area 38 Bearing pad 30′ Bearing pad interface 32′ Post 34′ Post base 34a′ Sensor web 40 First sensor 42 Second sensor 42a Third sensor 42b Fourth sensor 42c

DETAILED DESCRIPTION

Before the various embodiments of the present invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangements of components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that phraseology and terminology used herein with reference to device or element orientation (such as, for example, terms like “front”, “back”, “up”, “down”, “top”, “bottom”, and the like) are only used to simplify description of the present invention, and do not alone indicate or imply that the device or element referred to must have a particular orientation. In addition, terms such as “first”, “second”, and “third” are used herein and in the appended claims for purposes of description and are not intended to indicate or imply relative importance or significance.

Referring now to the drawings, wherein like reference numerals designate identical or corresponding parts throughout the several views, FIG. 1 provides an exploded view of a first embodiment of a compliant bearing configured as a groove thrust bearing 10. The bearing surface 20 of the groove thrust bearing 10 is show separated from a shaft collar 6, which shaft collar 6 is typically affixed to a rotatable shaft 4 as shown in FIG. 1. In operation, the shaft collar 6 is typically located very close to the bearing surface 20, separated therefrom by only a thin layer of lubricant, which lubricant may be gas, fluid, or other suitable lubricant. The illustrative embodiment of the groove thrust bearing 10 includes a main body 14, which is typically fixedly mounted to a support (not shown) during operation.

The embodiment of the groove thrust bearing 10 shown in FIGS. 1-1B includes a groove pattern 22 formed in the bearing surface 20. The pictured embodiment shows a groove pattern 22 configured as a spiral groove pattern 22. Other embodiments of the groove thrust bearing may have other groove patterns 22 without departing from the spirit and scope of the compliant bearing as disclosed and claimed herein.

The illustrative embodiment of a groove thrust bearing 10 is shown from a side vantage in FIG. 1A, and FIG. 1B provides a cross-sectional view thereof. The groove thrust bearing 10 may be formed with at least one bearing surface spring 24, 26 cooperatively engaging the main body 14 with the bearing surface 20. The illustrative embodiment includes a first bearing surface spring 24 oriented perpendicular to the rotational axis of the shaft 4 and a second bearing surface spring 26 oriented parallel to the rotational axis of the shaft 4. The first and second bearing surface springs 24, 26 may be integrally formed with one another, and/or integrally formed with the main body 14 and/or bearing surface.

Generally, the groove thrust bearing 10 disclosed herein provides axial compliant via the bearing surface springs 24, 26. This compliancy of the bearing surface allows the groove thrust bearing 10 to maintain a proper film thickness under a variety of conditions under which prior art bearings would fail. The groove thrust bearing 10 accomplishes this by allowing deformation and/or tilt of bearing surface 20 as needed based on perturbations from the shaft collar 6, groove thrust bearing 10, and/or lubricant.

The illustrative embodiment of a groove thrust bearing 10 shown herein utilizes four first bearing surface springs 24 and four second bearing surface springs 26, wherein each first bearing surface spring 24 is generally perpendicular with respect to each second bearing surface spring 26. However, other embodiments of the compliant bearing may use other numbers of first and second bearing surface springs 24, 26 (and associated elements) in different configurations and/or orientations without limitation.

As best shown in FIGS. 1A & 1B, the illustrative embodiment of a groove thrust bearing 10 includes a plurality of interstitial areas 28 to allow for a predetermined amount of motion of the bearing surface 20 and first and second bearing surface springs 24, 26 with respect to the main body 14. The illustrative embodiment includes a first interstitial area 28 between the bottom surface of the first bearing surface spring 24 and the main body 14, wherein either end of the first interstitial area 28 is formed with a generally circular cross-sectional shape. A second interstitial area 28 may be formed between the top surface of the first bearing surface spring 24 and the main body 14. The second interstitial area 28 may be interconnected with a third interstitial area 28 between the second bearing surface spring 26 and the main body 14, such that a portion of the main body 14 is cantilevered over a portion of the first bearing surface spring 24. Finally, a fourth interstitial area 28 may be formed between the bearing surface 20 and main body 14 opposite the groove pattern 22, as best shown in FIG. 1A.

The illustrative embodiment of the groove thrust bearing 10 having a spiral groove pattern 22 is known to have the best load capability among all hydrodynamic gas compliant bearings. However, a drawback of such compliant bearings is the potential to generate a negative damping at certain operating conditions (combination of speed and compliant load). The axial compliancy from the first and second bearing surface springs 24, 26 in cooperation with damping material 29 in certain interstitial areas 28 mitigates and in some cases eliminates any instability from negative damping by creating a positive resultant damping. This leads to increased load capacity compared to spiral groove bearings of the prior art.

A chart comparing the load capacity (in pounds) between prior art non-compliant spiral groove bearings and the illustrative embodiment of the groove thrust bearing 10 disclosed herein is shown in FIG. 4. As is readily apparent from FIG. 4, a prior art bearing may have a load capacity of less than 30 (thirty) pounds, while a comparable compliant bearing with integrated damping capability may achieve axial thrust loads in excess of 100 (one hundred) pounds. Additionally, through testing it has been determined that lower compliant capacity may result from misalignment of the shaft collar 6 and bearing surface 20 (or bearing pad interface 32), or if the shaft collar 6 operates at the threshold film thickness of negative damping. The compliant bearing as disclosed herein addresses such problems regarding static and/or dynamic misalignment/perturbation/distortion.

A second embodiment of a compliant bearing configured as a pad thrust bearing 12 is shown in FIGS. 2-3B. The illustrative embodiment includes four bearing pads 30 equally spaced about the main body 14 of the pad thrust bearing 12, as best shown in FIG. 3, which provides an axial view of the bearing pad interface 32 of each bearing pad 30 for the second embodiment of a compliant bearing.

The bearing pads 30 in the second embodiment of a compliant bearing are generally trapezoidal in shape, with the base and top edges being arcuate rather than linear. However, the bearing pads 30 may have any shape and/or configuration, and the scope of the compliant bearing as disclosed and claimed herein is in no way limited thereby. Additionally, the second embodiment of a compliant bearing utilizes four bearing pads 30 are used, and consequently, four pad radial springs 34 and four pad axial springs 36 are used. However, other embodiments of the compliant bearing may use other numbers of bearing pads 30 (and associated elements) without limitation.

As best shown in FIGS. 3A & 3B, as a corollary to the illustrative embodiment of the groove thrust bearing 10, the illustrative embodiment of a pad thrust bearing 12 includes a plurality of interstitial areas 38 to allow for a predetermined amount of motion of the bearing pads 30 and pad radial and axial springs 34, 36 with respect to the main body 14. The illustrative embodiment includes a first interstitial area 38 between the bottom surface of the pad radial spring 34 and the main body 14, wherein either end of the first interstitial area 38 is formed with a generally circular cross-sectional shape. A second interstitial area 38 may be formed between the top surface of the pad radial spring 34 and the main body 14. The second interstitial area 38 may be interconnected with a third interstitial area 38 between the pad axial spring 36 and the main body 14, such that a portion of the main body 14 is cantilevered over a portion of the pad radial spring 34. Finally, a fourth interstitial area 28 may be formed between the bearing pad 30 and main body 14 opposite the bearing pad interface, as best shown in FIG. 3A.

The optimal amount of compliancy will vary from one application to the next, and is therefore in no way limiting to the scope of any compliant bearing disclosed herein. Additionally, the configuration of the bearing surface springs 24, 26, pad radial spring 34, pad axial spring, interstitial areas 28, 38, and/or any damping material 29, 39 may be configured and/or oriented differently than as shown in the illustrative embodiments without departing from the spirit and scope of the compliant bearing as disclosed and claimed herein. Such alternative configurations and/or orientations may be required to achieve the optimal amount of compliancy for a given application.

The desired features for a specific compliant bearing may be achieved within a very short axial length by utilizing an EDM (Electrical Discharge Machine) technique. It is contemplated that the springs 24, 26, 34, 36 will typically be configured in pairs, which configuration is most compatible with the wire EDM cutting process through the main body 14 of the compliant bearing. In such a cutting process, two springs 24, 26, 34, 36 may be cut simultaneously due to the symmetry of the compliant bearing about it axial face. For example, as seen in FIG. 2, a total of four pairs of springs 34, 36 may be formed via two wire EDM cutting operations. It is also contemplated that the compliant bearings disclosed and claimed herein may be manufactured using alternative materials, such as polymers, plastics, other synthetic materials, and/or combinations thereof, certain of which may use injection molding or thermoforming.

The compliance feature of the groove thrust bearing 10 and pad thrust bearing 12 as disclosed herein as illustrative embodiments of a compliant bearing (which compliancy is provided by the first and second bearing surface springs 24, 26 and pad radial and axial springs 34, 36, respectively) may be implemented on any compliant bearings (e.g., spiral groove thrust bearing, conventional or flexure pivot tilt pad bearing, radially compliant bearing, etc.). Also, other types of springs 24, 26, 34, 36 other than leaf springs (such as those shown in the embodiments pictured herein) may be used with the compliant bearings disclosed and claimed herein to achieve the desired level of axial and/or radial compliancy.

In any embodiment of a compliant bearing, including but not limited to the illustrative embodiments of a groove thrust bearing 10 and pad thrust bearing 12 as disclosed herein, the compliant bearing may be configured with integrated damping capabilities. For example, as seen in FIG. 1C, a damping material 29 (e.g., a rubber, silicone, polymer material, etc.) may be positioned into various interstitial areas 28. Additionally, although not shown, radial compliant bearings and/or other axially compliant bearings (such as a pad thrust bearing 12) may be configured with integrated damping capabilities.

Any embodiment of a compliant bearing (including but not limited to a radially compliant bearing and the illustrative embodiments of a groove and pad thrust bearing 10, 12 shown herein), a sensor web 40 may be engaged with the compliancy members. Although the compliancy members for the illustrative embodiments of the groove thrust bearing 10 and pad thrust bearing 12 are shown herein as various springs 24, 26, 34, 36, FIGS. 5-5B show another embodiment of a compliant bearing configured as a multi-compliant bearing 16 wherein the compliancy members are configured as posts 34′.

FIG. 5 provides a perspective view of a plurality of bearing pads 30′ that may be used with the third embodiment of a compliant bearing. The bearing pads 30′ may include a post 34′ opposite the bearing pad interface 32′, which post 34′ may be integrally formed with the bearing pad 32′. The posts 34′ may terminate at a post base 34 a′ opposite the bearing pad interface 32′. The post base 34 a′ may cooperate with a main body to secure the bearing pads 30′ in relative special relation to one another within a predetermined amount of allowed movement.

As shown in detail in FIGS. 5A & 5B, sensors 42, 42 a, 42 b, 42 c may be secured to the post 34′ such that various forces experiences by the post 34′ (and consequently, various forces experiences by the bearing pad 30′) may be detected, and subsequently monitored and/or recorded. It is contemplated that the sensors 42, 42 a, 42 b, 42 c may be configured as strain gauges, and more specifically, electric strain gauges. However, any suitable sensor 42, 42 a, 42 b, 42 c may be used, and the optimal sensor 42, 42 a, 42 b, 42 c will vary from one application to the next.

Another embodiment of a sensor web 40 is shown in FIG. 6 as employed with the illustrative embodiment of the groove thrust bearing 10. Here, four sensors 42, 42 a, 42 c, 42 c are shown affixed to a second bearing surface spring 26, wherein the first and second sensors 42, 42 a are configured to detect deflection in the vertical direction (from the vantage shown in FIG. 6) and the second and third sensors 42 b, 42 c are configured to detect deflection in the horizontal direction (from the vantage shown in FIG. 6). Such a sensor web 40 may also be employed on any other spring 24, 34, 36 or other compliancy member of compliant bearings. In this configuration, the readings from the first and second sensors 42, 42 a and third and fourth sensors 42 b, 42 c, respectively, may be averaged or manipulated via an electric device. In other embodiments the sensor web 40 may be differently configured and/or configured to detect changes other than those of deflection, such as slope or other variables and/or parameters.

It is contemplated that the various sensors 42 in any given sensor web 40 may be configured to generate a data stream from data points created at specific intervals (e.g., time intervals). This data stream may be recorded and/or displayed in real time to a user who may then adjust the configuration of the compliant bearing to with which the sensor web 40 is employed, and/or adjust the operating parameters of the system with which the compliant bearing is utilized. Accordingly, the sensor web 40 may be beneficial in failure analysis of a compliant bearing and/or predicting failure or other various operating parameters of a compliant bearing. Such a sensor web 40 employed with an axial compliant bearing (such as a groove thrust bearing 10 or pad thrust bearing 12) may detect thrust load upon the bearing during rotation of the shaft 4 in either direction and/or start up thrust load during no rotation. Additionally, a sensor web 40 configured to measure mechanical deformation may be especially useful in determining the thrust force of various types of rotating equipment, including but not limited to turbo machinery.

The optimal dimensions and/or configuration of the main body 14, bearing surface 20, springs 24, 26, 34, 36, bearing pad 30, 30′, post 30′, post base 34 a′, and sensor web 40 will vary from one embodiment of the compliant bearing to the next, and are therefore in no way limiting to the scope thereof. The various elements of the compliant bearing may be formed of any material that is suitable for the application for which the compliant bearing is used. Such materials include but are not limited to metals and their metal alloys, polymeric materials, and/or combinations thereof.

Although the specific embodiments pictured and described herein pertain to a compliant bearing having four or eight or ten bearing pads 30, 30′, four first and second bearing surface springs 24, 26, and four pad radial and axial springs 34, 36, the compliant bearing may be configured with other orientations and/or with different quantities of the various elements having different shapes and/or orientations. Accordingly, the scope of the compliant bearing is in no way limited by the specific shape and/or dimensions of the main body 14, bearing surface 20, springs 24, 26, 34, 36, interstitial areas 28, 38, bearing pads 30, 30′, posts 34′, and/or post bases 34 a′ or the relative quantities and/or positions thereof.

Having described the preferred embodiments, other features, advantages, and/or efficiencies of the compliant bearing will undoubtedly occur to those versed in the art, as will numerous modifications and alterations of the disclosed embodiments and methods, all of which may be achieved without departing from the spirit and scope of the compliant bearing as disclosed and claimed herein. It should be noted that the compliant bearing is not limited to the specific embodiments pictured and described herein, but are intended to apply to all similar apparatuses for providing compliancy in a bearing, measuring parameters of a compliant bearing, and/or methods thereof. Modifications and alterations from the described embodiments will occur to those skilled in the art without departure from the spirit and scope of compliant bearing. 

The invention claimed is:
 1. A compliant bearing, comprising: a. a main body having a central bore formed therein, wherein said central bore is configured to allow a shaft to pass through said main body via said central bore, and wherein said shaft is rotatable with respect to said main body; b. a pad radial spring integrally formed with said main body, wherein said pad radial spring is oriented substantially perpendicular with respect to a rotational axis of said shaft; c. a pad axial spring integrally formed with said pad radial spring, wherein said pad axial spring is oriented substantially parallel with respect to said rotational axis of said shaft; d. a bearing pad engaged with said pad axial spring, wherein said pad radial spring provides compliance to said bearing pad in a dimension that is substantially normal with respect to said bearing pad interface; and e. an elastomeric damping material positioned adjacent said pad radial spring.
 2. The compliant bearing according to claim 1, wherein said compliant bearing further comprises a first interstitial area positioned between said main body and said pad radial spring, and wherein said elastomeric damping material is further defined as being positioned in said first interstitial area.
 3. The compliant bearing according to claim 2, wherein said compliant bearing further comprises a second interstitial area positioned between said bearing pad and said main body.
 4. The compliant bearing according to claim 3, wherein said compliant bearing further comprises a third interstitial area positioned between said pad axial spring and said main body.
 5. The compliant bearing according to claim 4, wherein said compliant bearing further comprises an elastomeric damping material positioned in said second and third interstitial areas.
 6. The compliant bearing according to claim 1, wherein said compliant bearing further comprises a sensor web integrated into said compliant bearing.
 7. The compliant bearing according to claim 6, wherein said sensor web is further defined as a first sensor engaged with said pad radial spring.
 8. The compliant bearing according to claim 7, wherein said sensor web is further defined as including a second sensor engaged with said pad axial spring.
 9. A compliant bearing comprising: a. a main body; b. a bearing pad having a bearing pad interface on a surface thereof, wherein said bearing pad interface is substantially planar; c. a first pad axial spring integrally formed with said main body and securing said bearing pad to said main body such that said bearing pad is compliant with respect to said main body in a direction parallel to a longitudinal axis of said compliant bearing; and, d. an elastomeric damping material positioned adjacent said first pad axial spring and said main body.
 10. The compliant bearing according to claim 9, wherein said compliant bearing further comprises: a. a second bearing pad; and b. a second pad axial spring integrally formed with said main body and securing said second bearing pad to said main body such that said second bearing pad is compliant with respect to said main body in a direction parallel to said longitudinal axis of said compliant bearing.
 11. The compliant bearing according to claim 10, wherein said compliant bearing further comprises: a. a first interstitial area positioned between said main body and said first pad axial spring; and b. a second interstitial area positioned between said main body and said second pad axial spring, wherein said elastomeric damping material is further defined as being positioned in said first interstitial area.
 12. The compliant bearing according to claim 11 wherein said elastomeric damping material is further defined as being positioned in said second interstitial area.
 13. The compliant bearing according to claim 12 wherein said elastomeric damping material is further defined as being positioned in said fourth interstitial area.
 14. The compliant bearing according to claim 11, wherein said compliant bearing further comprises a third and a fourth interstitial area positioned between said first and second bearing pads and said main body, respectively.
 15. The compliant bearing according to claim 14 wherein said elastomeric damping material is further defined as being positioned in said third interstitial area.
 16. The compliant bearing according to claim 14, wherein said compliant bearing further comprises a first pad radial spring engaged with said first pad axial spring and said first bearing pad.
 17. The compliant bearing according to claim 16, wherein said compliant bearing further comprises a fifth interstitial area positioned between said first pad radial spring and said main body.
 18. The compliant bearing according to claim 17, wherein said first pad axial spring and said first pad radial spring are further defined as being integrally formed with one another.
 19. The compliant bearing according to claim 18, wherein said compliant bearing further comprises a damping material positioned in said first interstitial area.
 20. The compliant bearing according to claim 19, wherein said compliant bearing further comprises a damping material positioned in said second, third, fourth, and fifth interstitial areas.
 21. The compliant bearing according to claim 16, wherein said compliant bearing further comprises a sensor web integrated into said compliant bearing.
 22. The compliant bearing according to claim 21, wherein said sensor web is further defined as a first sensor engaged with said first pad axial spring.
 23. The compliant bearing according to claim 22, wherein said sensor web is further defined as including a second sensor engaged with said first pad radial spring. 